WO2016028878A1 - Échangeur de chaleur à micro-canal à faible charge de réfrigérant - Google Patents

Échangeur de chaleur à micro-canal à faible charge de réfrigérant Download PDF

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Publication number
WO2016028878A1
WO2016028878A1 PCT/US2015/045866 US2015045866W WO2016028878A1 WO 2016028878 A1 WO2016028878 A1 WO 2016028878A1 US 2015045866 W US2015045866 W US 2015045866W WO 2016028878 A1 WO2016028878 A1 WO 2016028878A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
manifold
distributor
exchanger according
inner volume
Prior art date
Application number
PCT/US2015/045866
Other languages
English (en)
Inventor
Michael F. Taras
Tobias H. Sienel
Kazuo Saito
Arindom Joardar
Bruce J. Poplawski
Original Assignee
Carrier Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corporation filed Critical Carrier Corporation
Priority to ES15756314T priority Critical patent/ES2733236T3/es
Priority to CN201580044141.6A priority patent/CN106574808B/zh
Priority to EP15756314.9A priority patent/EP3183528B1/fr
Priority to EP19169594.9A priority patent/EP3537088B1/fr
Priority to US15/504,994 priority patent/US10288331B2/en
Publication of WO2016028878A1 publication Critical patent/WO2016028878A1/fr
Priority to US16/399,770 priority patent/US10753656B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates

Definitions

  • This disclosure relates generally to heat exchangers and, more particularly, to a microchannel heat exchanger for use in heat pump applications.
  • a heat pump can be utilized to heat air being delivered into an environment to be conditioned, or to cool and typically dehumidify the air delivered into the indoor environment.
  • a basic heat pump a heat pump
  • the compressor compresses a refrigerant and delivers it downstream through a refrigerant flow reversing device, typically a four- way reversing valve.
  • the refrigerant flow reversing device initially routes the refrigerant to an outdoor heat exchanger, if the heat pump is operating in a cooling mode, or to an indoor heat exchanger, if the heat pump is operating in a heating mode. From the outdoor heat exchanger, the refrigerant passes through an expansion device, and then to the indoor heat exchanger, in the cooling mode of operation. In the heating mode of operation, the refrigerant passes from the indoor heat exchanger to the expansion device and then to the outdoor heat exchanger. In either case, the refrigerant is routed through the refrigerant flow reversing device back into the compressor.
  • the heat pump may utilize a single bi-directional expansion device or two separate expansion devices.
  • These parallel flow heat exchangers are provided with a plurality of parallel heat transfer tubes, typically of a non-round shape, among which refrigerant is distributed and flown in a parallel manner.
  • the heat exchanger tubes typically incorporate multiple channels and are oriented substantially perpendicular to a refrigerant flow direction in the inlet and outlet manifolds that are in communication with the heat transfer tubes.
  • Heat transfer enhancing fins are typically disposed between and rigidly attached to the heat exchanger tubes.
  • a heat exchanger including a first manifold, a second manifold separated from the first manifold, and a plurality of heat exchanger tube arranged in spaced parallel relationship fluidly coupling the first and second manifolds.
  • a first end of each heat exchange tube extends partially into an inner volume of the first manifold and has an inlet formed therein.
  • a distributor is positioned within the inner volume of the first manifold. At least a portion of the distributor is arranged within the inlet formed in the first end of one or more of the plurality of heat exchange tubes.
  • the first manifold is configured to receive at least a partially liquid refrigerant.
  • a height of the first manifold is less than a width of the first manifold.
  • the first manifold is asymmetric about a horizontal plane extending there through.
  • the inlet formed in the first end is generally complementary to a contour of the distributor.
  • the inlet extends over only a portion of a width of the heat exchanger tube.
  • the distributor has an increased wall thickness to reduce the inner volume of the first manifold.
  • the distributor occupies between about 20% and about 60% of the inner volume of the first manifold.
  • the distributor occupies between about 30% and about 50% of the inner volume of the first manifold.
  • a porous structure is arranged within the inner volume of the manifold.
  • the distributor is arranged within the porous structure.
  • the porous structure has a porosity between about 30% and about 70%.
  • the porosity of the porous structure is non-uniform.
  • the porosity of the porous structure is increased to have localized flow resistance.
  • the porosity of the porous structure changes uniformly along the length of the first manifold.
  • the porous structure includes a plurality of cavities. Each cavity is configured to receive the first end of one of the plurality of heat exchanger tubes.
  • the first manifold is one of an inlet manifold and an intermediate manifold.
  • a spacer is positioned adjacent the distributor.
  • the spacer is configured to set a position of the distributor within the inner volume of the first manifold.
  • the spacer is configured to contact at least one of the plurality of heat exchanger tubes.
  • the spacer is configured to contact a portion of the first manifold inner wall.
  • the spacer extends over a portion of a length of the distributor.
  • the spacer includes a plurality of protrusions extending over at least a portion of a length of the distributor.
  • the distributor further comprises a groove formed in an exterior surface thereof.
  • the groove and an interior wall of the first manifold form a flow passage between a first manifold section and a second manifold section.
  • the groove comprises a plurality of separate grooves.
  • the groove comprises an interconnected groove.
  • the groove comprises a spiral pattern along a circumference of the distributor.
  • the groove is configured such that a fluid flowing through the groove is not directly injected into any of the plurality of heat exchanger tubes.
  • the flow direction imparted to a fluid flowing through the groove is not parallel with one or more of the plurality of heat exchanger tubes.
  • the groove comprises a plurality of grooves. A total cross-sectional flow area of the plurality of grooves is less than a cross-sectional flow area of the first manifold.
  • the total cross-sectional area is between 50% and 200% of a cross- sectional flow area of the first manifold section.
  • FIG. 1 is a schematic diagram of an example of a refrigeration system
  • FIG. 2 is a perspective view of a microchannel heat exchanger according to an embodiment of the present disclosure
  • FIG. 3 is a cross-sectional view of a microchannel heat exchanger according to an embodiment of the present disclosure
  • FIG. 4 is a cross-sectional view of a microchannel heat exchanger according to an embodiment of the present disclosure
  • FIG. 5 is a cross-section of a conventional manifold of the microchannel heat exchanger
  • FIG. 6 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 7 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 8 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 9 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 10 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 11 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 12 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 13 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 14 is a cross-section of another manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 15 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 16 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 17 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 18 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 19 is a cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure
  • FIG. 20 is another cross-section of a manifold of a microchannel heat exchanger having a reduced inner volume according to an embodiment of the present disclosure.
  • FIG. 21 is a perspective view of a portion of a distributor according to an embodiment of the present disclosure.
  • FIG. 1 An example of a vapor compression system 20 is illustrated in FIG. 1, including a compressor 22, configured to compress a refrigerant and deliver it downstream to a condenser 24. From the condenser 24, the cooled liquid refrigerant passes through an expansion device 26 to an evaporator 28. From the evaporator 28, the refrigerant is returned to the compressor 22 to complete the closed-loop refrigerant circuit.
  • the heat exchanger 30 configured for use in the vapor compression system 20 is illustrated in more detail.
  • the heat exchanger 30 is a single tube bank microchannel heat exchanger 30; however, microchannel heat exchangers having multiple tube banks are within the scope of the present disclosure.
  • the heat exchanger 30 includes a first manifold or header 32, a second manifold or header 34 spaced apart from the first manifold 32, and a plurality of heat exchange tubes 36 extending in a spaced parallel relationship between and connecting the first manifold 32 and the second manifold 34.
  • the first header 32 and the second header 34 are oriented generally horizontally and the heat exchange tubes 36 extend generally vertically between the two manifolds 32, 34.
  • the heat exchanger 30 may be used as either a condenser 24 or an evaporator 28 in the vapor compression system 20. By arranging the tubes 36 vertically, water condensate collected on the tubes 36 is more easily drained from the heat exchanger 30.
  • the heat exchanger 30 may be configured in a single pass arrangement, such that refrigerant flows from the first header 32 to the second header 34 through the plurality of heat exchanger tubes 36 in the flow direction indicated by arrow B (FIG. 2).
  • the heat exchanger 30 is configured in a multi-pass flow arrangement.
  • fluid is configured to flow from the first manifold 32 to the second manifold 34, in the direction indicated by arrow B, through a first portion of the heat exchanger tubes 36, and back to the first manifold 32, in the direction indicated by arrow C, through a second portion of the heat exchanger tubes 36.
  • the heat exchanger 30 may additionally include guard or "dummy" tubes (not shown) extending between its first and second manifolds 32, 34 at the sides of the tube bank. These "dummy" tubes do not convey refrigerant flow, but add structural support to the tube bank.
  • each heat exchange tube 36 comprises a flattened heat exchange tube having a leading edge 40, a trailing edge 42, a first surface 44, and a second surface 46.
  • the leading edge 40 of each heat exchanger tube 36 is upstream of its respective trailing edge 42 with respect to an airflow A through the heat exchanger 36.
  • the interior flow passage of each heat exchange tube 36 may be divided by interior walls into a plurality of discrete flow channels 48 that extend over the length of the tubes 36 from an inlet end to an outlet end and establish fluid communication between the respective first and second manifolds 32, 34.
  • the flow channels 48 may have a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section.
  • the heat exchange tubes 36 including the discrete flow channels 48 may be formed using known techniques and materials, including, but not limited to, extruded or folded.
  • a plurality of heat transfer fins 50 may be disposed between and rigidly attached, usually by a furnace braze process, to the heat exchange tubes 36, in order to enhance external heat transfer and provide structural rigidity to the heat exchanger 30,
  • Each folded fin 50 is formed from a plurality of connected strips or a single continuous strip of fin material tightly folded in a ribbon-like serpentine fashion thereby providing a plurality of closely spaced fins 52 that extend generally orthogonal to the flattened heat exchange tubes 36.
  • Heat exchange between the fluid within the heat exchanger tubes 36 and air flow A occurs through the outside surfaces 44, 46 of the heat exchange tubes 36 collectively forming the primary heat exchange surface, and also through the heat exchange surface of the fins 52 of the folded fin 50, which form the secondary heat exchange surface.
  • FIG. 5 An example of a cross-section of a conventional manifold 60, such as manifold 32 or 34 for example, is illustrated in FIG. 5.
  • the manifold 60 has a generally circular cross-section and the ends 54 of the heat exchanger tubes 36 are configured to extend at least partially into the inner volume 62 of the manifold 60.
  • a longitudinally elongated distributor 70 may be arranged within one or more chambers of the manifold 60.
  • the distributor 70 is arranged generally centrally within the inner volume of the manifold 62 and is configured to evenly distribute the flow of refrigerant between the plurality of heat, exchanger tubes 36 f!uidly coupled thereto.
  • the inner volume 62 of the manifold 60 must therefore be large enough to contain the tube ends 54 and a distributor 70 in a spaced apart relation such that an unobstructed fluid flow path exists from an inner volume 72 of the distributor 70 to an inner volume 62 of the manifold 60 and into the ends 54 of the heat exchanger tubes 36.
  • a manifold 60 of the heat exchanger such as a liquid manifold or a portion of a manifold configured to receive a liquid refrigerant for example, has a reduced inner volume 62 compared to the conventional manifold of FIG. 5.
  • the inner volume 62 of the manifold 60 is reduced by about 20% to about 60%, and more specifically by about 30% to about 50% depending on other operational and design parameters of the heat exchanger 20.
  • the inner volume 62 of the manifold 60 may be reduced by changing the shape of the end 54 of the heat exchanger tubes 36, by altering the cross-sectional shape of the manifold 60, or a combination including at least one of the foregoing. Such modifications can improve compactness of the heat exchanger and/or aid in positioning the distributor 70 within the manifold 60.
  • a generally concave inlet or cut 56 is formed in the end 54 of each of the heat exchange tubes 36 positioned within the manifold 60.
  • the cut 56 may have a curvature generally complementary to a curvature of the distributor 70, or may be different, as shown in FIG 7.
  • the cut 56 can extend over the entire width, or alternatively, over only a portion of the width of the heat exchanger tube 36 and is generally at least equal to the width of the distributor 70.
  • the distributor 70 is arranged within the inlet 56 formed the heat exchanger tube end 54.
  • the width of the manifold 60 must be at least equal to or greater than a width of the heat exchanger tubes 36 received therein.
  • the overall height of the manifold 60 may be reduced.
  • the cross-section of the manifold may be asymmetrical about a horizontal plane.
  • the contour curvature of an upper portion 64 and a lower portion 66 of the manifold 60 may be substantially different. As shown in the non-limiting embodiment illustrated in FIGS.
  • the upper portion 64 of the manifold 60 may be substantially semi-spherical in shape and the lower portion 66 of the manifold 60 may have a generally ellipsoid contour.
  • the manifold 60 is generally rectangular in shape.
  • the manifold 60 may be substantially D-shaped, such that the upper portion 64 of the manifold 60 is substantially flat and the lower portion 66 of the manifold 60 forms the general curved portion of the D.
  • the shapes of the distributors 70 and manifolds 60 illustrated and described herein are non-limiting, and other variations are within the scope of the present disclosure.
  • the inner volume 62 of the manifold 60 may also be reduced by increasing the thickness of the distributor wall 72 such that the distributor 70 itself occupies a larger portion of the inner volume 62.
  • the thickness of the distributor wall 76 is increased to occupy between about 20% and about 60% of the inner volume 62.
  • the interior volume 72 of the distributor 70, as well as the size and arrangement of the distributor holes 74 configured to distribute refrigerant from the distributor 70 to the inner volume 62 of the manifold 60 will generally remain unchanged.
  • the distributor 70 may be any type of distributor, including, but not limited to a circular distributor (FIG. 11), an ellipsoid distributor (FIG.
  • a distributor 70 having an increased wall thickness may also be used in conjunction with the method of reducing the inner volume 62 of the manifold 60 previously described.
  • a distributor plate 70 have an increased wall thickness may be arranged within a manifold 60 having a D-shaped cross- section as illustrated in FIG. 14, or a circular distributor 70 having an increased wall thickness may be at least partially arranged within the cut or inlet 56 formed in the ends 54 of the heat exchanger tubes 36.
  • a formed porous structure 80 may be positioned within the manifold 60 to reduce the inner volume 62 thereof.
  • the porous structure 80 be formed from a metal or non-metal material, such as a foam, mesh, woven wire or thread, or a sintered metal for example, and has a uniform or non-uniform porosity between about 30% and about 70%.
  • the porous structure 80 has a size and shape generally complementary to the inner volume 62 of the manifold 60.
  • the porosity of the porous structure 80 may be configured to change, such as uniformly for example, along the length of the manifold 60 in the direction of the refrigerant flow.
  • the porous structure 80 is formed with a plurality of pockets or cavities 82, each cavity 82 being configured to receive or accommodate one of the heat exchange tubes 36 extending into the manifold 60.
  • a distribution channel 84 may be formed over at least a portion of the length of the porous structure 80.
  • the size and shape of the distribution channel 84 may be constant or may vary and one or more side channels 86 may extend therefrom to uniformly distribute the refrigerant from the distribution channel 84 to each of the heat exchange tubes 36.
  • a distributor 70 having a plurality of distributor openings 74 may be inserted within the porous structure 80 (FIG. 16).
  • the porous structure 80 is configured to position and support the distributor 70 within the manifold 60.
  • the porous structure may include other provisions, such as relief pockets and enlarged clearances for example, may be added as necessary to maintain the integrity of the heat exchanger.
  • localized portions of the porous structure 80 may have an increased porosity to provide localized flow resistance.
  • the porous structure 80 may be integrally formed with the manifold 60, or alternatively, may be a separate removable sub-assembly inserted into the inner volume 62 of the manifold 60.
  • the porous structure 80 may be combined with any of the previously described systems having a reduced inner volume. For example, a distributor 70 having an increased wall thickness may be inserted into the porous structure 80, or the porous structure 80 may be added to a manifold 60 having a reduced height.
  • the vapor compression system 20 can be used in a heat pump application.
  • the vapor compression system may encompass auxiliary devices such as an accumulator, charge compensator, receiver, air management systems, or a combination including at least one of the foregoing.
  • auxiliary devices such as an accumulator, charge compensator, receiver, air management systems, or a combination including at least one of the foregoing.
  • one or more air management systems can be utilized to provide the airflow over an indoor and/or outdoor heat exchanger (e.g., condenser 24, evaporator 28, or an auxiliary heat exchanger configured to thermally communicate with the refrigerant circuit).
  • the one or more air management systems can facilitate heat transfer interaction between the refrigerant circulating throughout the refrigerant circuit and the indoor and/or outdoor environment respectively.
  • the distributor 70 may have a shape generally complementary to a portion of a cross-section of the manifold 60.
  • the distributor 70 has a generally rectangular body with curved edges complementary to the curvature of the manifold 60 at a certain location.
  • Refrigerant may be provided at a base of the manifold 60, as shown in FIG. 20, and is configured to pass through the plurality of distributor holes 74 formed in the distributor 70, for example in a vertical configuration, to one or more heat exchanger tubes 36.
  • a spacer 90 may be coupled to or integrally formed with a portion of the distributor 70 or the spacer 90 can be a separate component inserted into manifold 60.
  • the spacer 90 can be disposed between the distributor 70 and one or more tubes 36 (e.g., multiport tubes such as in a microchannel heat exchanger).
  • the spacer 90 may extend over only a portion of the length, or alternatively, over the full length of the distributor 70.
  • the spacer 90 includes a plurality of protrusions, such as arranged in a linear orientation for example, and positioned at intervals over the length of the distributor 70.
  • the spacer 90 can extend outward from a surface of the distributor 70 and can be configured to contact either a portion of one of more of the plurality of heat exchanger tubes 36, as shown in FIG. 19, or a portion of an internal wall of the manifold 60 to maintain a position of the distributor 70 relative to the tubes 36.
  • the spacer 90 can have any shape.
  • a cross-sectional shape of the spacer 90 can include circular, elliptical, or any polygonal shape having straight or curved sides.
  • the shape of the distributor 70 may be complementary to, and configured to contact, a portion of the manifold 60 or a tube 36 (e.g., contacting a solid portion adjacent to a port of a multiport tube, such as a web material between ports of a multiport tube) based on the overall distance between the spacer 90 and the tubes 36.
  • the one or more distributor holes 74 of previous embodiments formed in the distributor 70 may be formed as grooves 92 rather than holes 74.
  • the grooves 92 may be individual, or alternatively, may be connected to form a continuous groove in an external surface of the distributor 70.
  • the grooves 92 can have any shape.
  • the shape of the cross-sectional flow area of the grooves 92 can include circular, elliptical, or any polygonal shape having straight or curved sides.
  • the holes 74 are formed as a continuous groove 92 wrapped in a spiral configuration about a periphery of the distributor 70.
  • one or more dividers may be mounted to an exterior of the distributor 70 and configured to limit flow from the grooves 92 to one or more corresponding heat exchanger tubes 36.
  • the one or more grooves 92 formed in the distributor 70 are generally arranged at an angle to each of the plurality of heat exchanger tubes 36 such that one or more of the grooves do not directly face a corresponding tube 36. As a result, refrigerant from the grooves 92 is not directly injected into the plurality of tubes 36.
  • the configuration of each groove including the size and cross-sectional shape thereof, may be selected to control a flow of refrigerant from each groove 92 to a corresponding heat exchanger tube or tubes 36.
  • the distributor 70 can separate the inner volume of a manifold into a first manifold section 94 and a second manifold section 96.
  • the volume of the first manifold section 94 may be less than or equal to the volume of the second manifold section 96.
  • the one or more grooves 92 can define one of more flow passages between the first manifold section 94 and the second manifold section 96.
  • a total cross-sectional flow area of the one or more grooves 92 of the distributor 70 is generally less than the cross-sectional area of the manifold 60. In one embodiment, the total cross-sectional flow area of the one or more grooves 92 is between about 50% and about 200% of the cross-sectional area of a first manifold section 94 (see FIG.
  • the cross-sectional shape of the distributor 70 can be formed after the grooves 92 are formed into the distributor 70, such as through a machining process. In another embodiment, the distributor 70 can be formed into shape in a single operation (e.g., injection molding).
  • the various methods for reducing the inner volume 62 can provide significant benefits to the system at minima! additional cost.
  • reducing the inner volume 62 of a manifold 60 (e.g., an inlet, exit, or intermediate manifold) of a microchannel heat exchanger 20 the refrigerant charge of the heat exchanger 20 can be correspondingly reduced.
  • the present methods can be employed while maintaining or improving the refrigerant distribution to the tubes 36 of the heat exchanger.
  • heat exchangers 20 are compatible for use with lower global warming potential refrigerants.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un échangeur de chaleur comprenant un premier collecteur, un second collecteur séparé du premier collecteur, et plusieurs tubes d'échangeur de chaleur agencés selon une relation parallèle espacée couplant de manière fluidique le premier et le second collecteur. Une première extrémité de chaque tube d'échange de chaleur s'étend partiellement dans un volume interne du premier collecteur et comporte un orifice d'entrée. Un distributeur est positionné dans le volume interne du premier collecteur. Au moins une partie du distributeur est agencée dans l'orifice d'entrée formé dans la première extrémité d'un ou plusieurs tubes parmi la pluralité de tubes d'échange de chaleur.
PCT/US2015/045866 2014-08-19 2015-08-19 Échangeur de chaleur à micro-canal à faible charge de réfrigérant WO2016028878A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES15756314T ES2733236T3 (es) 2014-08-19 2015-08-19 Intercambiador de calor de micro canales de baja carga de refrigerante
CN201580044141.6A CN106574808B (zh) 2014-08-19 2015-08-19 低制冷剂充灌量微通道热交换器
EP15756314.9A EP3183528B1 (fr) 2014-08-19 2015-08-19 Échangeur de chaleur à micro-canal à faible charge de réfrigérant
EP19169594.9A EP3537088B1 (fr) 2014-08-19 2015-08-19 Échangeur de chaleur à micro-canal à faible charge de réfrigérant
US15/504,994 US10288331B2 (en) 2014-08-19 2015-08-19 Low refrigerant charge microchannel heat exchanger
US16/399,770 US10753656B2 (en) 2014-08-19 2019-04-30 Low refrigerant charge microchannel heat exchanger

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201462039154P 2014-08-19 2014-08-19
US62/039,154 2014-08-19
US201562161056P 2015-05-13 2015-05-13
US62/161,056 2015-05-13

Related Child Applications (2)

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US15/504,994 A-371-Of-International US10288331B2 (en) 2014-08-19 2015-08-19 Low refrigerant charge microchannel heat exchanger
US16/399,770 Continuation US10753656B2 (en) 2014-08-19 2019-04-30 Low refrigerant charge microchannel heat exchanger

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WO2016028878A1 true WO2016028878A1 (fr) 2016-02-25

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US (2) US10288331B2 (fr)
EP (2) EP3537088B1 (fr)
CN (1) CN106574808B (fr)
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FR3059414A1 (fr) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques Dispositif d’homogeneisation de la distribution d’un fluide refrigerant a l’interieur de tubes d’un echangeur de chaleur constitutif d’un circuit de fluide refrigerant
FR3077629A1 (fr) * 2018-02-07 2019-08-09 Atlantic Industrie Condenseur micro canaux optimise pour une charge minimale en fluide frigorigene
US11614260B2 (en) 2017-05-05 2023-03-28 Carrier Corporation Heat exchanger for heat pump applications

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ES2733236T3 (es) 2014-08-19 2019-11-28 Carrier Corp Intercambiador de calor de micro canales de baja carga de refrigerante
CN109099615A (zh) * 2017-06-21 2018-12-28 浙江盾安热工科技有限公司 一种微通道换热器
JP6888686B2 (ja) * 2017-10-18 2021-06-16 ダイキン工業株式会社 熱交換器及びそれを備えた空気調和装置
DE112019000761T5 (de) * 2018-03-30 2020-11-12 T.Rad Co., Ltd. Headerplattenloser wärmetauscher
CN111288833B (zh) * 2018-12-06 2022-03-15 丹佛斯有限公司 集流管组件以及换热器
CN112013710A (zh) * 2019-05-31 2020-12-01 浙江三花智能控制股份有限公司 分配管和换热器
CN112432542A (zh) * 2020-01-20 2021-03-02 杭州三花研究院有限公司 换热器

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FR3059414A1 (fr) * 2016-11-30 2018-06-01 Valeo Systemes Thermiques Dispositif d’homogeneisation de la distribution d’un fluide refrigerant a l’interieur de tubes d’un echangeur de chaleur constitutif d’un circuit de fluide refrigerant
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US11614260B2 (en) 2017-05-05 2023-03-28 Carrier Corporation Heat exchanger for heat pump applications
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EP3183528A1 (fr) 2017-06-28
ES2930816T3 (es) 2022-12-22
EP3183528B1 (fr) 2019-04-17
EP3537088A1 (fr) 2019-09-11
US10753656B2 (en) 2020-08-25
US10288331B2 (en) 2019-05-14
US20170276411A1 (en) 2017-09-28
CN106574808A (zh) 2017-04-19
CN106574808B (zh) 2020-04-07
EP3537088B1 (fr) 2022-10-26
US20190271492A1 (en) 2019-09-05
ES2733236T3 (es) 2019-11-28

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